Tripod joint having low vibration inducing forces

ABSTRACT

The invention relates to a tripod joint ( 1 ) comprising the following: an outer joint member ( 2 ) with several axially extending elongate tracks ( 4 ) formed therein and distributed over the inner circumference thereof; an inner joint member ( 3 ) with several radial axle journals ( 5 ) distributed over the outer circumference thereof; at least a number of rollers ( 6 ) corresponding to the number of axle journals ( 5 ), wherein the roller ( 6 ) is respectively pivotably retained with a central bore ( 20 ) on the associated axle journal ( 5 ) and is in engagement with the elongate tracks ( 4 ), wherein the roller ( 6 ) is displaceable in the associated track ( 4 ) in the axial direction of the outer joint member ( 2 ); wherein each axle journal ( 5 ) comprises on its circumference two outer diametrically opposed spherical end faces ( 16 ) for engagement into the bore ( 20 ). The joint is characterized in that the bore ( 20 ) has a cylindrical portion ( 9   c ) for engagement with the spherical end faces ( 16 ) in order to support the roller ( 6 ) so as to be displaceable relative to the axle journal ( 5 ), and at least a constricted portion ( 9   d,    9   e ) that is adjacent thereto in the axial direction, while forming a continuous transition, on one side of the cylindrical portion ( 9   c ), and that reaches behind the spherical end faces, for limiting the displacing movement.

The subject matter of the present invention is a tripod joint for a motor vehicle according to the preamble of claim 1 as well as a method for producing a tripod joint in accordance with the preamble of claim 10.

Tripod joints, which are also referred to as “constant velocity universal joints” (abbreviated CV joints) or also as “homokinetic joints” have long been known from the prior art. For example, they are used as internal joints for the drive shafts of front-wheel driven motor vehicles. They exhibit excellent constant-velocity properties and can be bent to angles of typically more than 10°. Furthermore, tripod joints can advantageously also be used for cardan shafts of rear-wheel driven or four-wheel driven motor vehicles. However, conventional tripod joints are problematic if the shafts are bent in an articulated manner relative to one another, i.e. if they form a working angle. Particularly in such a case it is important to avoid a relative sliding regarding the components that are in a rolling or roller contact. On the one hand, the large friction resistance accompanying this sliding leads to increased wear and increased power dissipation of the joint and, on the other hand, harbors the risk of the joint shaking. This not only reduces the life of the bearings of the shafts interconnected by the joints, but also affects the running smoothness of the vehicle.

Great efforts are being made to improve the running characteristics of tripod joints. For example, DE 41 301 83 A1 discloses a tripod joint in which a tilting of the outer ring in the track, e.g. in the case of a load introduction or change of a load, is supposed to be avoided by means of a special design of the tracks in the outer joint member and of the outer rings of the rollers. This rolling contact between the roller and the track of the outer joint member is not the subject matter of the present invention.

Other issues which are the subject matter of the present invention are the rolling contacts between the axle journal, hereinafter also referred to in short as axle journal, of the inner joint portion and the roller as well as the roller contacts of the components of the roller, which is usually configured as a roller bearing with an inner ring, an outer ring and several rolling elements.

For example, DE 102 06 733 A1 proposes a spherical-to-spherical contact surface between the axle journal and the roller, or the inner ring thereof, since it was assumed that the friction and thus the shaking would be reduced by a distribution of the Hertzian stress over as large a contact surface as possible. Surprisingly, however, the inventors of the present invention have found that the shaking increases due to this measure, i.e., that the vibration-inducing forces appear to increase.

Furthermore, it is known to realize constricted portions on the bore of the roller. These constricted portions mostly do not come into contact with the axle journal during the operation of the tripod joint, and merely serve as a form of mounting aid for securing the roller on the axle journal during assembly.

It is therefore the object of the present invention to provide a tripod joint with advantageous running characteristics, particularly with minimal shaking Furthermore, a method for producing an advantageous tripod joint is to be specified. This object is achieved by a tripod joint having the features of claim 1, as well by a method and the use according to the independent claims. Advantageous embodiments are in each case the subject matter of the dependent claims. It is to be noted that the features cited individually in the patent claims can be combined in any technologically meaningful manner and present other embodiments of the invention. The description, in particular in connection with the figures, additionally characterizes and specifies the invention.

The tripod joint according to the invention comprises an outer joint member, also referred to as tulip, with several axially extending elongate tracks formed therein and distributed over the inner circumference thereof. The tracks are, for example, incorporated as recesses into the inner wall of the outer joint member. The joint according to the invention, also referred to as tripod star, comprises an inner joint member with several, preferably three, circumferentially distributed radial axle journals. The joint according to the invention further comprises at least a number of rollers corresponding to the number, wherein the roller is respectively pivotably retained with a central bore on the associated axle journal and is in engagement with the elongate tracks of the outer joint member, wherein the roller is accommodated in the associated track so as to be displaceable in the axial direction of the outer joint member. The pivotability of the roller ensures that the roller maintains its orientation in the track of the outer joint member with respect to the track when the joint is bent and rotating and during its oscillation back and forth, which is the result of its bent state. According to the invention, the rolling surfaces of the tracks and of the rollers can be configured in any way. It is the responsibility of the person skilled in the art to select in this case the suitable configuration that is familiar from the prior art and that meets the requirements. “Axial” or “axial direction” relates to the corresponding axis of rotation of, for example, the outer joint member or of the inner joint member as well as of the roller.

Preferably, each axle journal comprises on its circumference two outer diametrically opposed spherical end faces for engagement into the bore of the roller.

According to the invention, moreover, it is provided that the bore has a cylindrical portion for engagement with the spherical end faces in order to support the roller so as to be displaceable relative to the axle journal. A constricted portion reaching behind the spherical end faces to limit the displacing movement is provided in the axial direction of the bore on at least one side of the cylindrical portion and adjacent thereto. The constricted portion means a tapering of the bore. For example, the tapered portion is provided on the side of the cylindrical portion facing towards the center of the inner joint portion, in order to prevent the separation of the roller from the axle journal. Alternatively, or preferably additionally, another constricted portion is provided on the, in the axial direction of the bore, opposite side of the cylindrical portion in order to limit the displacing movability of the roller in this direction and in order to prevent, for example, the roller from losing touching contact with the outer joint member.

According to the invention, it is furthermore provided that a continuous transition from the cylindrical portion to the constricted portion is provided in the axial direction of the bore. A cylindrical/spherical contact surface is provided in the cylindrical portion. According to the invention, it is provided that, in at least one position of the tripod joint, a touching contact is formed between the at least one constricted portion and the axle journal or the associated spherical end face. Thus, the terms constricted portion and spherical end face define such portions of the circumference of the respective component that are possible contact surfaces in at least one position of the tripod joint. This means that portions of the bore and the spherical contact surface situated so as to have no probability at all of any mutual contact can, according to the invention, be configured in any way or so as to correspond to the design requirements.

The term spherical end face is to be interpreted broadly and relates, for example, to end faces with any convex curvature; preferably, they are spherical and/or defined by a radius of curvature.

Surprisingly, it was found that, due to this configuration of the contact surface according to the invention, the vibration excitation, i.e. the shaking, in the extended orientation of the joint is minimized. The continuous transition provides for this advantage being maintained when the joint is bent, without having to relinquish the design advantage of the displacement limitation. For example, this design advantage is based on the fact that the tracks require no configuration that fixes the rollers in their axial direction. As was mentioned above, constricted portions are provided according to the invention that, on both sides, are continuously adjacent in the axial direction to the cylindrical portion.

In order to minimize shaking, concavely curved, particularly preferably spherical surface-shaped, constricted regions are provided.

Preferably, the constricted portion is formed complementary to the associated spherical end face. In that case, the axle journal radius nestles against the inner circumference of the constricted portion of the bore in a manner that preserves service life.

Preferably, the constricted portion and the associated spherical end face, i.e. the spherical end face with which the touching contact is established, have approximately the same radius of curvature. The ratio of the, if applicable smallest (for the case that this is not a purely spherical surface-shaped configuration), radius of curvature of the constricted portion (9 d, 9 e) and the, if applicable greatest, radius of curvature of the associated spherical end face (16) is between 1.00 and 1.01, preferably between 1.05 and 1.08, wherein the range boundaries are to be included in each case.

According to a preferred embodiment, the roller comprises an outer ring, an inner ring having the bore, and rolling elements interposed therebetween, wherein the outer ring is displaceable relative to the inner ring in the axial direction of the bore. Thus, an additional displaceability is provided besides the translational displaceability relative to the axle journal. This telescoping displacement has proved to be particularly advantageous in the prevention of shaking, particularly in the case of a bent joint. The length compensation of the axle journal/roller system required for a tripod joint to work, i.e. the displacement, is thus advantageously divided into two partial movements: there is an axle journal-side movement of the inner ring towards the axle journal, as well as a movement of the outer ring relative to the inner ring of the roller.

According to another preferred embodiment, it is provided that, at the latest when the tripod joint is bent to the maximum extent, the outer ring is displaced relative to the inner ring in the axial direction of the axle journal, and the inner ring on the axle journal, in relation to their positions when the tripod joint is not bent.

Preferably, the joint is configured in such a way that, when the tripod joint is bent increasingly from the non-bent position, the inner ring is displaced on the axle journal first, and then the outer ring is displaced relative to the inner ring in the axial direction of the axle journal.

For example, the inner ring moves first relative to the axle journal, due to the lower friction, and is thus the first part of a telescoping movement between the axle journal and the outer ring. Then, the axle journal radius nestles against the constricted portion of the inner ring in a “service life-friendly” manner and takes it with it. As described above, the axle journal-side displacement is functionally limited to the first bending range of the joint. The needle-side displacement is possible without any functional limitation. Due to the limitation to the inner ring-axle journal-displacement in the first bending range from the non-bent position, and thereafter to the outer ring-inner ring-displacement in the case of a greater degree of bending, it is ensured that only the first displacement, which is non-critical with regard to noise and vibration, takes place when the joint is being bent slightly, for example in the case of slight cornering, or during acceleration during straight travel, where a displacement takes place due to twisting. Thus, the driving comfort during acceleration of the motor vehicle is enhanced. In the case of the joint being bent to a great extent, which occurs due to the movement of the wheel suspension, another displacement is required which is then ensured via the displacing motion of the inner ring relative to the outer ring.

According to a preferred embodiment, it is provided that the maximum displacement of the inner ring relative to the axle journal in the axial direction of the axle journal is smaller than the maximum displacement of the outer ring relative to the inner ring in the axial direction of the axle journal.

Preferably, the ratio of the maximum displacement of the inner ring relative to the axle journal in the axial direction of the axle journal to the maximum displacement of the outer ring relative to the inner ring in the axial direction of the axle journal is less than 1:2, preferably less than 1:3. Still more preferably, the ratio is less than 1:3.3, such as, for example 1:3.48. For example, the maximum displacement is defined by the position of the geometric mean of the component or components concerned in the respective maximum position in relation to that position in the non-bent position of the tripod joint.

Particularly advantageous is an embodiment in which the maximum possible displacement of the rolling elements in the axial direction (relative to their rolling movement) relative to the inner ring is smaller than the maximum possible displacement of the rolling elements in the axial direction (relative to their rolling movement) relative to the outer ring. Preferably, the play of the rolling elements in the axial direction on the inner ring is limited to the minimum extent that is required for the rotary movement and/or that is due to processing.

Due to the small dimensions in the radial direction that results therefrom, the rolling elements are needles, wherein the movement of the needles in the axial direction relative to their rolling movement is limited by collar-like projections on the inner ring and/or the outer ring.

In order to minimize the risk of a vibration inducement due to the rolling movement of the rolling elements, the collar-like projections preferably form in the center of the axial end faces of the needles a contact surface therewith. Preferably, the end faces of the needles have a convex shape.

Preferably, the axle journal comprises flattened portions in each case in the circumferential direction between the spherical end faces; thus, the roller can easily be placed on the axle journal, if possible without any required deformation of the axle journal and/or the inner ring, for example by a pivoting movement.

Preferably, the tripod joint in one of the above-described embodiments is used in a motor vehicle. Due to the low vibration inducement resulting from the design according to the invention, it is used, for example, as an internal joint for the drive shafts of front-wheel driven motor vehicles, for cardan shafts of rear-wheel driven or four-wheel driven motor vehicles.

The invention in particular also relates to a method for deflecting a tripod joint comprising the following method steps:

A tripod joint in one of the above-described embodiments is provided. It comprises, for example, an outer joint member, with several circumferentially distributed axially extending elongate tracks formed therein; an inner joint member with several circumferentially distributed radial axle journals, and at least a number of rollers corresponding to the number of axle journals, wherein the roller is respectively pivotably retained with a central bore on the associated axle journal and is in engagement with the elongate tracks, and wherein the roller is displaceable in the track in the axial direction of the outer joint member; wherein each axle journal comprises on its circumference two outer diametrically opposed spherical end faces for engagement into the bore; and wherein the bore has a cylindrical portion for engagement with the spherical end faces in order to support the roller so as to be displaceable relative to the axle journal, and at least a constricted portion that is adjacent thereto in the axial direction, while forming a continuous transition, on one side of the cylindrical portion and that reaches behind the spherical end faces, for limiting the displacing movement.

The method moreover comprises a step of bending the tripod joint in which at least one position is reached in which the one constricted portion of the bore comes into touching contact with the associated spherical end face of the axle journal.

According to a preferred variant of the method, it is provided that the roller comprises an outer ring, an inner ring having the bore, and rolling elements interposed therebetween, wherein the outer ring is displaceable relative to the inner ring in the axial direction of the bore. Thus, an additional displacement is carried out during the step of bending, in addition to the translational displacement relative to the axle journal. This telescoping displacement has proved to be particularly advantageous in the prevention of shaking, particularly in the case of a bent joint. The length compensation of the axle journal/roller system required for a tripod joint to work, i.e. the displacement, is thus advantageously divided into two partial movements: there is an axle journal-side movement of the inner ring towards the axle journal, as well as a movement of the outer ring relative to the inner ring of the roller.

Preferably, the joint is configured in such a way that, when the tripod joint is bent increasingly from the non-bent position, the inner ring is displaced on the axle journal first, and then the outer ring is displaced relative to the inner ring in the axial direction of the axle journal.

The invention as well as the technical environment are explained in more detail below with reference to the figures. It must be remarked that the Figures depict a particularly preferred embodiment of the invention, but that it is not limited thereto. The Figures schematically show:

FIG. 1: a perspective partial cross-sectional view of a first exemplary embodiment of a tripod joint 1 according to the invention;

FIG. 2: an exploded view of the tripod joint according to the invention from FIG. 1;

FIG. 3: a cross-sectional view of the roller 6 of the tripod joint 1 according to the invention from FIG. 1,

FIG. 4: a cross-sectional view for illustrating the bore geometry of the inner ring of the roller of the tripod joint according to the invention from FIG. 1.

In a schematic representation, FIGS. 1 and 2 show an exemplary embodiment of a tripod joint 1 according to the invention in a perspective view and exploded view, respectively. The outer joint member 2 comprises an axis of rotation defining the axial direction of the outer joint member, and is opened on one side. At its closed end, the outer joint member 2 leads into a shaft 11 for connection to, for example, a drive output shaft, which is not shown, of a transmission of a motor vehicle. Three tracks 4 extending along the axial direction are formed in the outer joint member 2. Each track 4 forms two running surfaces disposed opposite from each other, on which the rollers 6 inserted into the track 4 roll, one of which rollers is shown in FIG. 1 in a sectional view for illustration purposes. The roller 6 comprises an inner ring 9, an outer ring 7 which is engagement with the track 6, and needles 8 interposed between the rings 7, 9 as rolling elements. As is further apparent from FIG. 1, each roller 6 is retained on an axle journal 5 of the inner joint member 3, which is also referred to as tripod star and which is inserted into the outer joint member 2. As FIG. 2 shows, the axle journal 5 comprises two diametrically opposed spherical end faces 16 for engagement with the inner surface of the bore 20 of the respective inner ring 9 of the roller 6. In order to facilitate assembly, the axle journal 5 is flattened between the spherical end faces 16 in the circumferential direction. These flattened portions 17 permit the placement of the rollers 6 by a pivoting movement. Once they are in engagement with the inner ring 9, this “partially spherical” design of the axle journals 5 permits, among other things, a pivoting of the rollers 6 relative to the axle journals 5.

The tripod star 3 has an inner recess 10 in whose inner wall a plurality of splines is formed for connection of a connecting shaft not shown, for example to a ball slip joint. The axis of rotation of the shaft or of the inner joint member 3 defines the axial direction of the inner joint member 3. As is shown in FIG. 1, the joint 1 enables bending between the shaft 11 and the axis of rotation of the inner joint member 3, the pivoting degree of freedom is indicated by the arrow 12. In the bent position, the axle journals 5, during the rotation of the joint 1, execute an oscillating movement in the tracks 4 indicated by the double arrow 13. At the same time, the outer rings 7 of the rollers 6 rotate about their inner rings 9, as the double arrow 15 illustrates. The special configuration of the bore 20 of the inner rings 9, which is described below, permits a displacement of the inner rings relative to the axle journal in the radial direction of the outer joint member 2, as is indicated by the arrow 14.

An additional displaceability 19 of the outer ring 7 relative to the inner ring 9 in the direction parallel to their axis of rotation results from its design configuration, which can be seen in FIG. 3. The inner ring 9 defines a running surface for the needles 8 as rolling elements. The rolling elements 8 are kept in the running track by collar-like projections 9 a, 9 b running peripherally along the edge of the outer circumference. The collar-like projections 9 a, 9 b are configured so as to respectively form an almost point-shaped contact surface in the center 18 of their end faces, i.e. in the axis of rotation. The inner circumferential surface of the outer ring 7, which forms a running surface together with the rolling elements 8, has an extent exceeding the width of the needles 8 and enables a displacement of the outer ring 7 relative to the needles 8, parallel to their rolling direction. In the non-assembled state of the joint 1, this displacing movement is limited only in one direction by the unilateral collar-like projection 7 a on the outer ring 7.

It becomes clear from FIG. 4 that the inner circumferential surface provided by the bore 20 in the inner ring 9, which is in engagement with the spherical end faces 16 of the axle journal 5 from FIG. 2, comprises three portions. A middle cylindrical portion 9 c as well as two constricted portions 9 d, 9 e that are continuously adjacent to this portion 9 c. These concavely formed constricted portions 9 d and 9 e defined by spherical surfaces reach behind the spherical end faces 16 of the axle journals 5 if the axes of rotation of the roller 6 concerned are oriented parallel to the axial direction of the axle journals 5. Only upon exceeding a predetermined degree of pivoting of the roller 6 relative to the axle journal 5 does the axle journal 5 come out of engagement, and the roller 6 can be separated from the axle journal 5. Given a corresponding orientation of the rollers 6 in a predetermined pivoting range about this previously mentioned parallel orientation, it is thus fixed on the axle journal 5. The cylindrical portion 9 c provides for a cylinder/spherical contact between the axle journal 5 and the inner ring 9; at the same time, a displaceability of the inner ring 9 relative to the axle journal 5 in the extension direction of the axle journal 5 is enabled. 

1.-15. (canceled)
 16. A tripod joint, comprising an outer joint member with several axially extending elongate tracks formed therein and distributed over the inner circumference thereof; an inner joint member with several radial axle journals distributed over the outer circumference thereof; at least a number of rollers corresponding to the number of axle journals, wherein the roller is respectively pivotably retained with a central bore on the associated axle journal and is in engagement with the elongate tracks, wherein the roller is displaceable in the associated track in the axial direction of the outer joint member; wherein each axle journal comprises on its circumference two outer diametrically opposed spherical end faces for engagement into the bore; wherein the bore has a cylindrical portion for engagement with the spherical end faces in order to support the roller so as to be displaceable relative to the axle journal, and at least a constricted portion that is adjacent thereto in the axial direction, while forming a continuous transition, on one side of the cylindrical portion and that reaches behind the associated spherical end face, for limiting the displacing movement, and wherein the constricted portion is disposed in such a way that, at least in one position of the tripod joint, the constricted portion rests against the axle journal, wherein the roller comprises an outer ring, an inner ring having the bore, and rolling elements optionally interposed therebetween, and characterised in that the outer ring is displaceable relative to the inner ring in the axial direction of the axle journal, and that the tripod joint is configured in such a way that, at the latest when the tripod joint is bent to the maximum extent, the outer ring is displaced relative to the inner ring in the axial direction of the axle journal, and the inner ring is displaced on the axle journal, in relation to their positions when the tripod joint is not bent, and that, when the tripod joint is bent increasingly from the non-bent position, the inner ring is displaced on the axle journal first, and then the outer ring is displaced relative to the inner ring in the axial direction of the axle journal.
 17. The tripod joint according claim 16, wherein the constricted portion is formed by a concavely curved, spherical surface-shaped, region.
 18. The tripod joint according to claim 16, wherein the constricted portion is formed complementary to the associated spherical end face.
 19. The tripod joint according to claim 16, wherein the ratio of the, if applicable smallest, radius of curvature of the constricted portion and the, if applicable greatest, radius of curvature of the associated spherical end face is between 1.00 and 1.01, with the range boundaries being included in each case.
 20. The tripod joint according to claim 16, wherein the bore comprises two constricted portions that are adjacent thereto in the axial direction, while forming a continuous transition, on one side of the cylindrical portion, and that reach behind the associated spherical end face, for limiting the displacing movement.
 21. The tripod joint according to claim 16, wherein the maximum displacement of the inner ring relative to the axle journal in the axial direction of the axle journal is smaller than the maximum displacement of the outer ring relative to the inner ring in the axial direction of the axle journal.
 22. The tripod joint according to claim 16, wherein the ratio of the maximum displacement of the inner ring relative to the axle journal in the axial direction of the axle journal to the maximum displacement of the outer ring relative to the inner ring in the axial direction of the axle journal is less than 1:2.
 23. The tripod joint according to claim 16, wherein the maximum possible displacement of the rolling elements relative to the inner ring in the axial direction is smaller than the maximum possible displacement in the axial direction of the rolling elements relative to the outer ring.
 24. The tripod joint according to claim 16, wherein the rolling elements are needles and the movement of the needles in the axial direction, relative to their rolling movements, is limited by collar-like projections on the inner ring and/or the outer ring.
 25. The tripod joint according to claim 24, wherein the collar-like projections (9 a, 9 b) form, in the centre of the axial end face of the needles, a contact surface therewith.
 26. The tripod joint according to claim 25, wherein the end faces of the needles have a convex shape.
 27. The tripod joint according to claim 16, wherein the joint is disposed in a motor vehicle. 